WO2016058457A1 - 使双端面机械密封摩擦副冷却的轴套及其离心泵冷却*** - Google Patents

使双端面机械密封摩擦副冷却的轴套及其离心泵冷却*** Download PDF

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WO2016058457A1
WO2016058457A1 PCT/CN2015/088357 CN2015088357W WO2016058457A1 WO 2016058457 A1 WO2016058457 A1 WO 2016058457A1 CN 2015088357 W CN2015088357 W CN 2015088357W WO 2016058457 A1 WO2016058457 A1 WO 2016058457A1
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Prior art keywords
ring
sleeve
bushing
seal
passage
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PCT/CN2015/088357
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English (en)
French (fr)
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邢宇
邢天宜
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邢宇
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Publication of WO2016058457A1 publication Critical patent/WO2016058457A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal

Definitions

  • the invention relates to a cooling system for a centrifugal pump.
  • API682 Appendix D (Standard Appendices)
  • the standard flushing scheme and the auxiliary metal components contain the double-end mechanical seal flushing scheme.
  • the cooling liquid phase in the vicinity of the media end mechanical seal friction pair is relatively static for the friction source.
  • API 682 Appendix D (Standard Appendix)
  • the standard seal flushing plan 52 in the auxiliary metal components as an example.
  • the purpose of this scheme is to cool and remove the friction generated by the media end mechanical seal friction pair during operation. Heat and heat transferred from a part of the medium. However, sometimes the local high temperature can not be eliminated, especially the fluid with low saturated vapor pressure. The frictional heat will not dissipate in time, and there will be flashing phenomenon.
  • the short-lived gas state will impact the dynamic and static ring of the mechanical seal friction pair. Even push the moving and static rings away from each other in an instant. It is like an explosion between the static and dynamic rings of a mechanical seal. At this point, a leak will occur. Once the leak occurs, the friction pair is immediately cooled, and the gaseous state material disappears immediately. At this time, the mechanical seal and the static pressure ring are mechanically sealed by the spring force of the mechanical seal and the medium pressure (ie, the closing force). suddenly fitted and collided; then flashing appeared again, and the moving and static rings again caused an impact. Repeatedly, from beginning to end, the cycle is not finished until the mechanical seal is completely damaged.
  • the technical problem to be solved by the present invention is to provide a bushing for cooling a double-end mechanical seal friction pair and a centrifugal pump cooling system thereof, which can make the double-end mechanical seal medium end abut against the friction pair, which is a heat source.
  • the part of the coolant flows in the axial direction of the sleeve, so that this part of the liquid is continuously convectively cooled there.
  • a sleeve for cooling the double-end mechanical seal friction pair comprising a sleeve sleeve sleeved on the outer side of the pump shaft of the centrifugal pump, at both ends of the inner circumference of the sleeve a left sealing ring and a right sealing ring are respectively disposed between the pump shafts, and the left sealing ring and the right sealing ring are respectively embedded on the inner circumferential surface of the sleeve,
  • a fifth passage capable of circulating a cooling liquid is formed between the inner peripheral surface of the sleeve and the outer peripheral surface of the pump shaft, and the fifth passage is formed by an axis formed between the left seal ring and the right seal ring
  • a groove is formed on the inner side wall, and a fourth passage connecting the fifth passage and the cooling liquid passage outside the sleeve is formed on the sleeve and adjacent to the medium end seal moving ring.
  • the fifth passage formed between the outer peripheral surface of the pump shaft and the inner circumferential surface of the sleeve is formed along the axial direction of the pump shaft.
  • a centrifugal pump cooling system having a sleeve for cooling a double-end mechanical seal friction pair, comprising a pump casing, a pump shaft partially located inside the pump casing and having a sleeve sleeve on the outer side, and sequentially connected to one of the pump casings a first sealing gland and a second sealing gland which are sleeved on the sleeve and form a space with the sleeve, are disposed between the sleeve and the pump casing and are opposite to the bushing a fixedly connected media end sealing moving ring, a medium end sealing static ring disposed between the sleeve and the first sealing gland and fixedly connected with the first sealing gland, the medium end sealing static ring and
  • the medium end sealing moving ring is a contact connection, an atmospheric end sealing moving ring disposed in a space between the sleeve and the second sealing gland and fixedly connected with the sleeve, and the second sealing
  • the cooling liquid circulation passage includes a first passage formed in the first sealing gland and the upper port is connected to the heat inlet or the outlet of the heat exchanger through an external pipeline.
  • the pumping ring seventh passage is formed in the second sealing gland and the upper port is connected to the eighth passage of the heat exchanger liquid outlet or the liquid inlet through an external pipeline.
  • the fifth passage formed between the outer circumferential surface of the pump shaft and the inner circumferential surface of the sleeve is formed on the left side seal ring and the right side seal ring between the outer peripheral surface of the pump shaft and the inner circumferential surface of the sleeve
  • a groove on the inner side wall of the sleeve, the left seal ring and the right side seal ring are respectively embedded on the inner peripheral surface of the sleeve.
  • the fifth passage formed between the outer peripheral surface of the pump shaft and the inner circumferential surface of the sleeve is formed along the axial direction of the pump shaft.
  • the bush sleeve for cooling the double-end mechanical seal friction pair and the centrifugal pump cooling system thereof can make the double-end mechanical seal medium end of the centrifugal pump abut against the friction pair, and the position of the heat source is positively beneficial to the flow passage of the coolant Above, let that part of the coolant flow in the axial direction of the sleeve, so that this part of the liquid is continuously convectively cooled here. Therefore, the leakage caused by the flash phenomenon of the friction pair of the mechanical seal medium end of the centrifugal pump is completely eliminated.
  • FIG. 1 is a schematic structural view of a convection cooling system of a prior art centrifugal pump
  • FIG. 2 is a schematic structural view of a convection cooling system of a friction end of a double-end mechanical seal medium of a centrifugal pump of the present invention
  • FIG. 3 is a schematic view showing the structure of a shaft convection cooling system of the present invention.
  • Throttle ring 8 second sealing gland
  • the bushing for cooling the double-end mechanical seal friction pair and the centrifugal pump cooling system thereof are arranged in the standard flushing scheme of the original standard API682 Appendix D (standard appendix) and the standard seal flushing plan in the auxiliary metal component.
  • the mechanical seal bushing is modified (as shown in Fig. 2). That's it.
  • the sleeve for cooling the double-end mechanical seal friction pair of the present invention includes a sleeve 2 sleeved on the outer side of the pump shaft 1 of the centrifugal pump, at both ends of the inner circumference of the sleeve 2
  • a left side seal ring 14 and a right side seal ring 15 are respectively disposed between the pump shaft 1 and the right side seal ring 15 and the right side seal ring 15 are respectively embedded in the inner circumferential surface of the sleeve 2
  • a fifth passage 205 capable of circulating a cooling liquid is formed between the inner circumferential surface of the sleeve 2 and the outer circumferential surface of the pump shaft 1, and the fifth passage 205 is formed by the left sealing ring.
  • the fifth passage 205 is connected to the fourth passage 204 of the cooling liquid passage outside the sleeve 2.
  • the fifth passage 205 formed between the outer peripheral surface of the pump shaft 1 and the inner peripheral surface of the boss 2 is formed along the axial direction of the pump shaft 1.
  • the centrifugal pump cooling system of the present invention having a bushing for cooling the double-end mechanical seal friction pair includes a pump casing 5 partially located in the pump casing 5 and having an outer sleeve.
  • the pump shaft 1 of the sleeve 2 is sequentially connected to one side of the pump casing 5 and sleeved on the sleeve 2 and forms a space with the first sealing gland 6 and the second sealing gland a medium end sealing ring 3 disposed between the sleeve 2 and the pump casing 5 and fixedly connected to the sleeve 2, disposed between the sleeve 2 and the first sealing gland 6 and
  • the first sealing gland 6 is a fixedly connected media end sealing static ring 4, and the medium end sealing static ring 4 is in contact connection with the medium end sealing moving ring 3, and is disposed on the sleeve 2 and the second sealing.
  • the cover 8 is fixedly connected to the atmospheric end seal static ring 11
  • the atmospheric end seal moving ring 10 is in contact connection with the atmospheric end seal static ring 11
  • the pump effect ring 9 sleeved on the outside of the atmospheric end seal ring 10
  • a throttle ring 7 fixedly connected to the first sealing gland 6 is disposed in a space between the sleeve 2 and the first sealing gland 6, at the first sealing gland 6 and the media end
  • a seal static ring 4, a throttle ring 7, a medium end seal moving ring 3, a sleeve 2, a pump shaft 1, an atmospheric end seal moving ring 10, and a second seal gland 8 are formed by connecting an external pipe 12
  • the external heat exchanger 13 can enable the heat exchange liquid to flow directly along the axial direction of the rotating member while simultaneously rotating along the axial direction of the rotating member to the contact surface B of the medium end seal static ring 4
  • the cooling liquid circulation passage includes a first communication gland which is formed on the first sealing gland 6 and the upper port is connected to the liquid inlet or the liquid outlet of the heat exchanger 13 through the external pipe 12 a passage 201, a second passage 202 formed between the throttle ring 7 and the medium end seal static ring 4, formed on the medium end seal moving ring 3 and the medium end seal static ring 4 and the a third passage 203 between the sleeves 2, a fourth passage 204 formed in the sleeve 2 near the side of the medium end sealing ring 3, formed on the pump shaft 1 and the sleeve a fifth passage 205 between 2, the fifth passage 205 formed between the outer circumferential surface of the pump shaft 1 and the inner circumferential surface of the sleeve 2 is formed along the axial direction of the pump shaft 1, and The fifth passage 205 formed between the outer circumferential surface of the pump shaft 1 and the inner circumferential surface of the sleeve 2 is formed on the left side seal ring 14 and the right side between the outer circumferential surface of the
  • the grooves on the inner side wall of the sleeve 2 between the side seal rings 15 are respectively embedded in the inner peripheral surface of the sleeve 2, respectively.
  • the eighth passage 208 of the liquid inlet is also a sixth passage 206 integrally formed in the sleeve 2 and between the throttle ring 7 and the atmospheric end sealing ring 10, formed at the atmospheric end sealing ring 10 and the Between the second sealing glands 8 and through the seventh passage 207 of the pumping ring 9, formed in the second sealing gland 8 and the upper port is connected to the outlet of the heat exchanger 13 through the external pipe 12. Or the eighth passage 208 of the liquid inlet.
  • the sleeve of the present invention for cooling the double-end mechanical seal friction pair and its centrifugal pump cooling system, the mechanical seal sleeve and the pump shaft are made with a fluid passage, and the fluid flows there to form a closed loop. That is, the position B in Fig. 2 is beneficial on the route of the cooling fluid flow, so that the friction pair of the mechanical seal of the medium end (the friction surface between the medium end sealing ring 3 and the medium end sealing ring 4) is fully obtained. Convection cooling from the cooling fluid. Arranging a throttle ring 7 in the sealed chamber between the two inlets and the outlet port of the heat exchanger 13 causes the cooling fluid to flow into the sealed chamber and mostly flows in the designed cooling liquid circulation passage.
  • the cooling fluid flows out through the heat exchanger 13 and flows through the first passage 201 in sequence to cool the first sealing gland 6; when flowing through the second passage 202, the first sealing gland 6 and the medium end seal static ring respectively 4.
  • the throttle ring 7 and the sleeve 2 are cooled; when flowing through the third passage 203, the medium end seal static ring 4 and the medium end seal moving ring 3 (especially the medium end seal static ring 4 and the medium end seal)
  • the moving ring 3 is at the friction surface B between them) and the sleeve 2 is cooled; when flowing through the fourth passage 204, the medium end sealing moving ring 3, the sleeve 2 and the pump shaft 1 are cooled; flowing through the fifth passage
  • the pump shaft 1 and the sleeve 2 are cooled; when flowing through the sixth passage 206 and the seventh passage 207, respectively, the throttle ring 7, the atmospheric end seal ring 10, the pump effect ring 9, and the first seal gland 6 are respectively Cooling with the second sealing gland 8; the second sealing gland

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Mechanical Sealing (AREA)

Abstract

一种使双端面机械密封摩擦副冷却的轴套，包括套在离心泵的泵轴（1）外侧的轴套（2），在轴套（2）内周面的两端与泵轴（1）之间分别设置有左侧密封圈（14）和右侧密封圈（15），左侧密封圈（14）和右侧密封圈（15）分别嵌入在轴套（2）的内周面上，轴套（2）的内周面与泵轴（1）外周面之间形成有流通冷却液体的第五通道（205），在轴套（2）上且临近介质端密封动环（3）处对应第五通道（205）形成有连通第五通道（205）与轴套（2）外侧的冷却液体通道的第四通道（204）。还公开了包括该轴套的离心泵冷却***。该冷却***能够让离心泵的双端面机械密封介质端靠着摩擦副的位置正好处在冷却液的流通通道上，让冷却液顺着轴套的轴向方向流动起来，使冷却液产生对流冷却，从而彻底消除因离心泵机械密封介质端摩擦副所出现闪蒸现象而发生的泄露。

Description

使双端面机械密封摩擦副冷却的轴套及其离心泵冷却*** 技术领域
本发明涉及一种离心泵的冷却***。特别是涉及一种使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***。
背景技术
API682附录D(标准性附录)中标准冲洗方案和辅助金属构件里含有双端面机械密封冲洗方案***里介质端机械密封摩擦副附近地区的冷却液相对于摩擦副这个发热源的位置是相对静止，以API682附录D(标准性附录)中标准冲洗方案和辅助金属构件中标准密封冲洗计划52作为例子，这种方案的目的是为了冷却并且带走介质端机械密封摩擦副在工作中所产生的摩擦热和一部分介质传过来的热量。但有时仍然消除不了瞬间局部高温，尤其是输送饱和蒸气压较低的流体，摩擦热及时散不出去会出现闪蒸现象而出现短时间气体状态的物质去冲击机械密封摩擦副的动、静环，甚至于瞬间把动、静环相互推开。就好像在机械密封的动静环之间产生***一样。此时将产生泄漏，一旦泄漏，摩擦副立刻得到冷却，气体状态的物质立刻消失，这时在机械密封的弹簧力和介质压力(也就是闭合力)双重作用下机械密封的动、静环又突然贴合而发生碰撞；然后闪蒸又出现了，动、静环又再次造成冲击。周而复始，始而复周，循环起来没完，直到机械密封彻底损坏。这种情况非常普遍，一旦出现，不但使得泄漏量增加，而且机械密封很快就会失效。更换机械密封费事又费钱，如果问题没得到彻底解决，即便更换了新的机械密封，很快还会损坏。
以图1所示的现有技术API682附录D(标准性附录)中标准冲洗方案和辅助金属构件里标准密封冲洗计划52和计划53所采用的面对背安装的双端面机械密封(液体缓冲双接触式湿密封2CW-CW和液封液面对背结构的接触式湿密封3CW-FB)作为例子进行阐述。其中附图标记A所指的位置是双端面机械密封介质端紧靠着摩擦副最需要的到冷却的部位，在现有技术中冷却液体在此处仅仅是跟着泵轴同步原地旋转，不产生轴向流动，可以说这部分冷却液体与泵轴、轴套和机械密封动、静环的相互位置永远相对静止。由于冷却液体始终在原地保持不动，所以无法依靠对流的方式冷却介质端机械密封的摩擦副，总是让介质端机械密封动环和机械密封静环之间的摩擦处于出现闪蒸温度条件的临界点，造成机械密封非正常损坏。
发明内容
本发明所要解决的技术问题是，提供一种使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***，能够让双端面机械密封介质端紧靠着摩擦副这个产生热源的位置正好处在冷却液的流动通道上，让那一部分冷却液顺着轴套的轴向方向流动起来，使得这一部分液体不断在这里产生对流冷却。
本发明所采用的技术方案是：一种使双端面机械密封摩擦副冷却的轴套，包括有套在离心泵的泵轴外侧的轴套，在所述的轴套内周面的两端与所述的泵轴之间分别设置有左侧密封圈和右侧密封圈，所述的左侧密封圈和右侧密封圈分别嵌入在所述轴套的内周面上，所述的 轴套的内周面与所述的泵轴外周面之间形成有能够流通冷却液体的第五通道，所述的第五通道是由形成在左侧密封圈和右侧密封圈之间的轴套内侧壁上的凹槽构成，在所述轴套上且临近介质端密封动环处对应所述第五通道形成有连通所述第五通道与轴套外侧的冷却液体通道的第四通道。
所述的形成在泵轴外周面和轴套内周面之间的第五通道是沿所述泵轴的轴向形成。
一种具有使双端面机械密封摩擦副冷却的轴套的离心泵冷却***，包括有泵壳，部分位于所述的泵壳内且外侧套有轴套的泵轴，依次连接在泵壳的一侧且套在所述轴套上并与所述的轴套形成有一定空间的第一密封压盖和第二密封压盖，设置在轴套与泵壳之间且与所述的轴套为固定连接的介质端密封动环，设置在轴套与第一密封压盖之间且与所述的第一密封压盖为固定连接的介质端密封静环，所述的介质端密封静环与所述的介质端密封动环为接触连接，设置在轴套与第二密封压盖之间的空间内且与所述的轴套为固定连接的大气端密封动环和与所述第二密封压盖固定连接的大气端密封静环，所述的大气端密封动环与所述的大气端密封静环为接触连接，套在所述大气端密封动环外侧的泵效环，在轴套与第一密封压盖之间的空间内设置有与所述的第一密封压盖固定连接的节流环，在所述的第一密封压盖、介质端密封静环、节流环、介质端密封动环、轴套、泵轴、大气端密封动环以及第二密封压盖之间形成有一条通过外部管路连接位于外部的热交换器且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动对介质端密封静环和介质端密封动环的接触面能够直接进行热交换的冷却液体循环通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖上且上端口通过外部管路连接所述热交换器进液口或出液口的第一通道，形成在所述的节流环和介质端密封静环之间的第二通道，形成在所述的介质端密封动环和介质端密封静环与所述的轴套之间的第三通道，形成在所述的轴套内且靠近介质端密封动环一侧的第四通道，形成在所述的泵轴外周面和所述的轴套内周面之间的第五通道，一体形成在所述的轴套内以及所述的节流环与大气端密封动环之间的第六通道，形成在所述的大气端密封动环与所述的第二密封压盖之间并贯穿所述的泵效环第七通道，形成在所述的第二密封压盖且上端口通过外部管路连接所述热交换器出液口或进液口的第八通道。
所述的形成在泵轴外周面和轴套内周面之间的第五通道是形成在位于所述泵轴外周面与轴套内周面之间的左侧密封圈和右侧密封圈之间的轴套内侧壁上的凹槽，所述的左侧密封圈和右侧密封圈分别嵌入在所述轴套的内周面上。
所述的形成在泵轴外周面和轴套内周面之间的第五通道是沿所述泵轴的轴向形成。
本发明的使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***，能够让离心泵的双端面机械密封介质端紧靠着摩擦副这个产生热源的位置正好处在冷却液的流动通道上，让那一部分冷却液顺着轴套的轴向方向流动起来，使得这一部分液体不断在这里产生对流冷却。从而彻底消除因离心泵机械密封介质端摩擦副所出现闪蒸现象而发生的泄漏。
附图说明
图1是现有技术离心泵的对流冷却***结构示意图；
图2是本发明的离心泵的双端面机械密封介质端摩擦副的对流冷却***结构示意图；
图3是本发明轴部对流冷却***结构示意图。
1：泵轴                            2：轴套
3：介质端密封动环                  4：介质端密封静环
5：泵壳                            6：第一密封压盖
7：节流环                          8：第二密封压盖
9：泵效环                          10：大气端密封动环
11：大气端密封静环                 12：外部管路
13：热交换器                       14：左侧密封圈
15：右侧密封圈                     201：第一通
202：第二通道                      203：第三通道
204：第四通道                      205：第五通道
206：第六通道                      207：第七通道
208：第八通道
具体实施方式
下面结合实施例和附图对本发明的使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***做出详细说明。
本发明的使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***，是在原有标准API682附录D(标准性附录)中标准冲洗方案和辅助金属构件里标准密封冲洗计划中配置双端面机械密封的***所采用的双端面机械密封基础上，仅仅在其机械密封的两个端面之间再增加一节流机构，与此同时把机械密封的轴套改造一下(如图2所示)就可以了。
如图3所示，本发明的使双端面机械密封摩擦副冷却的轴套，包括有套在离心泵的泵轴1外侧的轴套2，在所述的轴套2内周面的两端与所述的泵轴1之间分别设置有左侧密封圈14和右侧密封圈15，所述的左侧密封圈14和右侧密封圈15分别嵌入在所述轴套2的内周面上，所述的轴套2的内周面与所述的泵轴1外周面之间形成有能够流通冷却液体的第五通道205，所述的第五通道205是由形成在左侧密封圈14和右侧密封圈15之间的轴套2内侧壁上的凹槽构成，在所述轴套2上且临近介质端密封动环3处对应所述第五通道205形成有连通所述第五通道205与轴套2外侧的冷却液体通道的第四通道204。所述的形成在泵轴1外周面和轴套2内周面之间的第五通道205是沿所述泵轴1的轴向形成。
如图2、图3所示，本发明的具有使双端面机械密封摩擦副冷却的轴套的离心泵冷却***，包括有泵壳5，部分位于所述的泵壳5内且外侧套有轴套2的泵轴1，依次连接在泵壳5的一侧且套在所述轴套2上并与所述的轴套2形成有一定空间的第一密封压盖6和第二密封压盖8，设置在轴套2与泵壳5之间且与所述的轴套2为固定连接的介质端密封动环3，设置在轴套2与第一密封压盖6之间且与所述的第一密封压盖6为固定连接的介质端密封静环4，所述的介质端密封静环4与所述的介质端密封动环3为接触连接，设置在轴套2与第二密封压盖8之间的空间内且与所述的轴套2为固定连接的大气端密封动环10和与所述第二密封压 盖8固定连接的大气端密封静环11，所述的大气端密封动环10与所述的大气端密封静环11为接触连接，套在所述大气端密封动环10外侧的泵效环9，在轴套2与第一密封压盖6之间的空间内设置有与所述的第一密封压盖6固定连接的节流环7，在所述的第一密封压盖6、介质端密封静环4、节流环7、介质端密封动环3、轴套2、泵轴1、大气端密封动环10以及第二密封压盖8之间形成有一条通过外部管路12连接位于外部的热交换器13且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动对介质端密封静环4和介质端密封动环3的接触面B能够直接进行热交换的冷却液体循环通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖6上且上端口通过外部管路12连接所述热交换器13进液口或出液口的第一通道201，形成在所述的节流环7和介质端密封静环4之间的第二通道202，形成在所述的介质端密封动环3和介质端密封静环4与所述的轴套2之间的第三通道203，形成在所述的轴套2内且靠近介质端密封动环3一侧的第四通道204，形成在所述的泵轴1和所述的轴套2之间的第五通道205，所述的形成在泵轴1外周面和轴套2内周面之间的第五通道205是沿所述泵轴1的轴向形成的，并且，所述的形成在泵轴1外周面和轴套2内周面之间的第五通道205是形成在位于所述泵轴1外周面与轴套2内周面之间的左侧密封圈14和右侧密封圈15之间的轴套2内侧壁上的凹槽，所述的左侧密封圈14和右侧密封圈15分别嵌入在所述轴套2的内周面上。还有一体形成在所述的轴套2内以及所述的节流环7与大气端密封动环10之间的第六通道206，形成在所述的大气端密封动环10与所述的第二密封压盖8之间并贯穿所述的泵效环9第七通道207，形成在所述的第二密封压盖8且上端口通过外部管路12连接所述热交换器13出液口或进液口的第八通道208。
本发明的使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***，机械密封轴套与泵轴之间制作有流体通道，并且让流体从此处流过去而形成闭合回路。即图2中位置B的地方正好处在冷却流体流动的路线上，这样就使得介质端机械密封的摩擦副(介质端密封动环3和介质端密封静环4之间的摩擦面)充分得到来自冷却流体的对流冷却。在热交换器13的进液口和出液口这两个通道之间的密封腔内布置有节流环7就使得冷却流体进入密封腔后大部分按照设计好的冷却液体循环通道内流动，走完全部路程以后再从冷却液体循环通道的出液口流出，基本上避免了流体刚从进液口进来马上超短路就从出液口流走，因为在这个过程中没有进行冷却过程。此处用机械密封也可以，但是用节流环代替机械密封能节省轴向空间、结构简单、成本低、加工周期短。
本发明的使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***的工作过程如下：
冷却流体经热交换器13流出，依次流经第一通201时，对第一密封压盖6进行冷却；流经第二通道202时，分别对第一密封压盖6、介质端密封静环4、节流环7和轴套2进行冷却；流经第三通道203时，分别对介质端密封静环4、介质端密封动环3(尤其是对介质端密封静环4和介质端密封动环3它们之间的摩擦面B点处)和轴套2进行冷却；流经第四通道204时对介质端密封动环3、轴套2和泵轴1进行冷却；流经第五通道205时对泵轴1、轴套2进行冷却；流经第六通道206和第七通道207时，分别对节流环7、大气端密封动环10、泵效环9、第一密封压盖6和第二密封压盖8进行冷却；流经第八通道208时对第二密封压盖8 进行冷却，最后冷却流体从第八通道208流出通过外部管路12流入热交换器13进行热交换后，又从热交换器13流出与离心泵进行下一轮的热交换，如此循环。

Claims (6)

  1. 一种使双端面机械密封摩擦副冷却的轴套，包括有套在离心泵的泵轴(1)外侧的轴套(2)，在所述的轴套(2)内周面的两端与所述的泵轴(1)之间分别设置有左侧密封圈(14)和右侧密封圈(15)，所述的左侧密封圈(14)和右侧密封圈(15)分别嵌入在所述轴套(2)的内周面上，其特征在于，所述的轴套(2)的内周面与所述的泵轴(1)外周面之间形成有能够流通冷却液体的第五通道(205)，所述的第五通道(205)是由形成在左侧密封圈(14)和右侧密封圈(15)之间的轴套(2)内侧壁上的凹槽构成，在所述轴套(2)上且临近介质端密封动环(3)处对应所述第五通道(205)形成有连通所述第五通道(205)与轴套(2)外侧的冷却液体通道的第四通道(204)。
  2. 根据权利要求1所述的使双端面机械密封摩擦副冷却的轴套，其特征在于，所述的形成在泵轴(1)外周面和轴套(2)内周面之间的第五通道(205)是沿所述泵轴(1)的轴向形成。
  3. 一种具有权利要求1或2所述的使双端面机械密封摩擦副冷却的轴套的离心泵冷却***，包括有泵壳(5)，部分位于所述的泵壳(5)内且外侧套有轴套(2)的泵轴(1)，依次连接在泵壳(5)的一侧且套在所述轴套(2)上并与所述的轴套(2)形成有一定空间的第一密封压盖(6)和第二密封压盖(8)，设置在轴套(2)与泵壳(5)之间且与所述的轴套(2)为固定连接的介质端密封动环(3)，设置在轴套(2)与第一密封压盖(6)之间且与所述的第一密封压盖(6)为固定连接的介质端密封静环(4)，所述的介质端密封静环(4)与所述的介质端密封动环(3)为接触连接，设置在轴套(2)与第二密封压盖(8)之间的空间内且与所述的轴套(2)为固定连接的大气端密封动环(10)和与所述第二密封压盖(8)固定连接的大气端密封静环(11)，所述的大气端密封动环(10)与所述的大气端密封静环(11)为接触连接，套在所述大气端密封动环(10)外侧的泵效环(9)，其特征在于，在轴套(2)与第一密封压盖(6)之间的空间内设置有与所述的第一密封压盖(6)固定连接的节流环(7)，在所述的第一密封压盖(6)、介质端密封静环(4)、节流环(7)、介质端密封动环(3)、轴套(2)、泵轴(1)、大气端密封动环(10)以及第二密封压盖(8)之间形成有一条通过外部管路(12)连接位于外部的热交换器(13)且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动对介质端密封静环(4)和介质端密封动环(3)的接触面(B)能够直接进行热交换的冷却液体循环通道。
  4. 根据权利要求3所述的具有使双端面机械密封摩擦副冷却的轴套的离心泵冷却***，其特征在于，所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖(6)上且上端口通过外部管路(12)连接所述热交换器(13)进液口或出液口的第一通道(201)，形成在所述的节流环(7)和介质端密封静环(4)之间的第二通道(202)，形成在所述的介质端密封动环(3)和介质端密封静环(4)与所述的轴套(2)之间的第三通道(203)，形成在所述的轴套(2)内且靠近介质端密封动环(3)一侧的第四通道(204)，形成在所述的泵轴(1)外周面和所述的轴套(2)内周面之间的第五通道(205)，一体形成在所述的轴套(2) 内以及所述的节流环(7)与大气端密封动环(10)之间的第六通道(206)，形成在所述的大气端密封动环(10)与所述的第二密封压盖(8)之间并贯穿所述的泵效环(9)第七通道(207)，形成在所述的第二密封压盖(8)且上端口通过外部管路(12)连接所述热交换器(13)出液口或进液口的第八通道(208)。
  5. 根据权利要求4所述的具有使双端面机械密封摩擦副冷却的轴套的离心泵冷却***，其特征在于，所述的形成在泵轴(1)外周面和轴套(2)内周面之间的第五通道(205)是形成在位于所述泵轴(1)外周面与轴套(2)内周面之间的左侧密封圈(14)和右侧密封圈(15)之间的轴套(2)内侧壁上的凹槽，所述的左侧密封圈(14)和右侧密封圈(15)分别嵌入在所述轴套(2)的内周面上。
  6. 根据权利要求4或5所述的具有使双端面机械密封摩擦副冷却的轴套的离心泵冷却***，其特征在于，所述的形成在泵轴(1)外周面和轴套(2)内周面之间的第五通道(205)是沿所述泵轴(1)的轴向形成。
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CN113028064B (zh) * 2021-03-18 2022-08-12 北京航天石化技术装备工程有限公司 一种高压炉水循环泵机械密封及降压降温***、方法
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0290752A2 (de) * 1987-05-11 1988-11-17 Feodor Burgmann Dichtungswerke GmbH & Co. Gleitringdichtung mit einer Kühleinrichtung
EP0723099A1 (de) * 1995-01-23 1996-07-24 KSB Aktiengesellschaft Gleitringdichtung für Kesselspeisepumpen
CN201166122Y (zh) * 2007-12-13 2008-12-17 丹东克隆集团有限责任公司 波纹管机械密封装置
CN203770645U (zh) * 2014-01-06 2014-08-13 东莞市华汇精密机械有限公司 一种双端面机械密封装置
CN104265907A (zh) * 2014-10-15 2015-01-07 邢宇 双端面机械密封介质端摩擦副的对流冷却
CN204553314U (zh) * 2014-10-15 2015-08-12 邢宇 使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2308032A1 (fr) * 1976-04-14 1976-11-12 Sigma Vyzkumny Ustav Cerpacich Dispositif d'etancheite hydrodynamique axial a anneau de glissement avec capillaires detendeurs a chemises de refroidissement
FR2712936B1 (fr) * 1993-11-24 1996-02-09 Latty Int Boîte d'étanchéïté perfectionnée pour pompe et son application notamment à une pompe alimentaire de centrale électrique.
DE10012663B4 (de) * 2000-03-15 2012-08-02 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Merbelsrod Kühlmittelpumpe mit elektronisch kommutiertem Eletromotor
DE10040211C2 (de) * 2000-08-17 2002-10-17 B & V Industrietechnik Gmbh Vorrichtung zur Abdichtung von Antriebswellen
JP3782690B2 (ja) * 2001-08-31 2006-06-07 イーグル工業株式会社 メカニカルシール装置
CN2711469Y (zh) * 2004-06-11 2005-07-20 新疆乌苏市北方新科有限公司 轻烃泵用机械密封装置
DE102011118294B3 (de) * 2011-11-10 2013-04-18 Eagleburgmann Germany Gmbh & Co. Kg Gleitringdichtungsanordnung mit Tesla-Pumpe
CN103216466B (zh) * 2013-04-12 2015-07-08 丹东克隆集团有限责任公司 泵用串联式机械密封装置及其泵送环
CN103233909A (zh) * 2013-04-12 2013-08-07 丹东克隆集团有限责任公司 泵用串联式机械密封装置的泵送环
CN204226640U (zh) * 2014-08-18 2015-03-25 四川日机密封件股份有限公司 用于高温高压旋转机械的密封装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0290752A2 (de) * 1987-05-11 1988-11-17 Feodor Burgmann Dichtungswerke GmbH & Co. Gleitringdichtung mit einer Kühleinrichtung
EP0723099A1 (de) * 1995-01-23 1996-07-24 KSB Aktiengesellschaft Gleitringdichtung für Kesselspeisepumpen
CN201166122Y (zh) * 2007-12-13 2008-12-17 丹东克隆集团有限责任公司 波纹管机械密封装置
CN203770645U (zh) * 2014-01-06 2014-08-13 东莞市华汇精密机械有限公司 一种双端面机械密封装置
CN104265907A (zh) * 2014-10-15 2015-01-07 邢宇 双端面机械密封介质端摩擦副的对流冷却
CN204553314U (zh) * 2014-10-15 2015-08-12 邢宇 使双端面机械密封摩擦副冷却的轴套及其离心泵冷却***

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107401617B (zh) * 2017-08-24 2023-03-28 合肥恒大江海泵业股份有限公司 一种用于转轴的组合式密封装置
CN107401617A (zh) * 2017-08-24 2017-11-28 合肥恒大江海泵业股份有限公司 一种用于转轴的组合式密封装置
CN107642486A (zh) * 2017-10-26 2018-01-30 佛山市科达液压机械有限公司 一种新型柱塞泵静压支撑侧盖
CN107642486B (zh) * 2017-10-26 2024-03-12 佛山市科达液压机械有限公司 一种新型柱塞泵静压支撑侧盖
CN107676485A (zh) * 2017-11-07 2018-02-09 昆山密友机械密封有限公司 高温卧式机械密封结构
CN107676485B (zh) * 2017-11-07 2024-04-16 昆山密友机械密封有限公司 高温卧式机械密封结构
CN108457865A (zh) * 2018-03-21 2018-08-28 浙江南元泵业有限公司 耐高温泵及其冷却结构
CN108457865B (zh) * 2018-03-21 2024-03-08 南元泵业有限公司 耐高温泵及其冷却结构
CN108386545A (zh) * 2018-04-17 2018-08-10 江苏浩特隆搅拌设备有限公司 带机架式双端面机械密封装置
CN108386545B (zh) * 2018-04-17 2024-02-09 江苏浩特隆搅拌设备有限公司 带机架式双端面机械密封装置
CN109488770A (zh) * 2018-12-20 2019-03-19 丹东克隆集团有限责任公司 核电站安全壳热量导出泵用双端面机械密封装置
CN110030383A (zh) * 2019-04-10 2019-07-19 艾志（南京）环保管接技术股份有限公司 内带轴向浮动托盘套的液体用机械密封
CN110500411A (zh) * 2019-09-04 2019-11-26 上海创异流体机械有限公司 一种可靠的塑料泵用机械密封装置
CN111097354A (zh) * 2019-12-27 2020-05-05 上海聚友化工有限公司 一种用于聚合釜的传动端
CN112096873A (zh) * 2020-07-31 2020-12-18 中核核电运行管理有限公司 核电站流体动压型主泵机械密封的浮动密封装置
CN111911632A (zh) * 2020-07-31 2020-11-10 中核核电运行管理有限公司 核电站流体动压型主泵机械密封的密封组件
CN111810644A (zh) * 2020-07-31 2020-10-23 中核核电运行管理有限公司 核电站流体动压型主泵机械密封的随动密封结构
CN112398261A (zh) * 2020-11-23 2021-02-23 山东淄泵泵业有限公司 免维护低噪音高效电机
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CN116222941A (zh) * 2023-05-08 2023-06-06 福建福清核电有限公司 一种核主泵机械密封试验台密封面径向振动模拟装置

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